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WO2012032164A1 - Procéder pour commander un compresseur - Google Patents

Procéder pour commander un compresseur Download PDF

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Publication number
WO2012032164A1
WO2012032164A1 PCT/EP2011/065662 EP2011065662W WO2012032164A1 WO 2012032164 A1 WO2012032164 A1 WO 2012032164A1 EP 2011065662 W EP2011065662 W EP 2011065662W WO 2012032164 A1 WO2012032164 A1 WO 2012032164A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
control
model
state
theoretical
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2011/065662
Other languages
German (de)
English (en)
Inventor
Georg Winkes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to US13/820,812 priority Critical patent/US20130173063A1/en
Priority to EP11757265.1A priority patent/EP2598754A1/fr
Priority to CN201180043721.5A priority patent/CN103097737B/zh
Priority to RU2013115761/06A priority patent/RU2570301C2/ru
Publication of WO2012032164A1 publication Critical patent/WO2012032164A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
    • G05B15/00—Systems controlled by a computer
    • G05B15/02—Systems controlled by a computer electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/007—Conjoint control of two or more different functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0284—Conjoint control of two or more different functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0292—Stop safety or alarm devices, e.g. stop-and-go control; Disposition of check-valves
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05B—CONTROL OR REGULATING SYSTEMS IN GENERAL; FUNCTIONAL ELEMENTS OF SUCH SYSTEMS; MONITORING OR TESTING ARRANGEMENTS FOR SUCH SYSTEMS OR ELEMENTS
    • G05B17/00—Systems involving the use of models or simulators of said systems
    • G05B17/02—Systems involving the use of models or simulators of said systems electric

Definitions

  • the invention relates to a method for controlling a compressor.
  • Compressors for providing compressed gas for industrial purposes are usually controlled by means of one or more maps. From DE 195 06 790 A such a method for controlling a compressor is known, in which by means of sensors of the compressor actual values of the
  • Compressor are measured and from these measurements and a default value for the throughput, the isentropic
  • Compressor work and the inlet flow rate is determined. Using a map stored in a computer efficiency-optimized control values for the angular positions of the nozzles during operation of the compressor are gradually adjusted.
  • EP 1 069 314 AI a compressor control known.
  • EP 1 069 314 A1 proposes for this purpose a setpoint value
  • US 2009/0274565 A1 discloses a method for controlling a compressor, in which current measured values for three parameters of the compressor are determined. Based on three characteristics of the compressor - each map describes the relationship between two of these parameters - working points of the compressor are determined for the current measured values. It is an object of the present invention to provide a
  • the invention is based on a method for controlling a compressor. According to the invention, the method comprises the following steps:
  • the inventive design a good efficiency and a large driving range of the compressor can be advantageously achieved. Furthermore, energy consumption can be kept cost-saving low.
  • each of the expert appears reasonable sense compressor, such as a motor-driven, in particular
  • Multi-stage compressor with intermediate cooling and constant speed and / or a turbine-driven gear compressor or single-shaft compressor can be understood.
  • a "setpoint" is here in particular a
  • a distance to a surge line For example, a distance to a surge line, a
  • Pinion shafts of the compressor a compliance with the intake limits of individual stages of the compressor, holding a
  • Control means a part of the compressor or an external one
  • control values of the control elements are expediently taken from a data memory, e.g. from a map, or calculated. You can each have a state of
  • Indicate actuator e.g. a position of a valve or the like, the state usually not the
  • control unit which for this purpose each, the Professional for judiciously considered investigation or
  • the setpoint value to be maintained is passed to the method as a secondary condition.
  • the determined control values are transmitted by the control unit to a model unit.
  • control values and the control elements can have different or the same parameters or different or the same
  • model-based theoretical state here represents in particular a state that is based on a
  • Computational model of the model unit and in particular based on a thermodynamic model is determined.
  • a behavior of the compressor is simulated to determine the theoretical state.
  • the model unit calculates with the transmitted control values on the basis of the thermodynamic model expediently what a state of the compressor would be if these control values were set on the control elements and the compressor would be operated with these parameters. This can be independent of direct changes to the compressor
  • Compressor can be determined. In addition, fluctuations in a flow rate during operation can be advantageously prevented.
  • Determining the state can also be understood as a determination that is undirected and / or diffuse and / or also "false "and / or in particular according to a numerical method of sequential quadratic programming.”
  • the control loop is preferably located between the control unit and the model unit
  • Model unit the information of the determined theoretical state or an associated parameter to the
  • Control unit determines this from, at a
  • At least one of the actuating elements is only actuated with a control value when a parameter of the theoretical state corresponding to the desired value reaches a predetermined proximity to the desired value.
  • a predetermined proximity to the desired value should be understood to mean, in particular, that a value is present in the control unit
  • Optimization function of the method relates.
  • the expert selects the value of the given proximity adapted to the
  • an "actual value of the state of the compressor” should in particular be a measured and / or momentary or current state value of the compressor, such as a pressure
  • Expert for pertinent state value understood that is located in a time window of less than 60 seconds, preferably less than 30 seconds, and more preferably less than 10 seconds from the time of determination removed.
  • one and more preferably at least two temperatures go into the calculation or into the thermodynamic model and in particular an inlet temperature or a measured suction temperature of the compressor or a first stage of the compressor and a measured recooling temperature of the compressor or the first stage, which corresponds to a suction temperature of at least a second stage of the compressor.
  • the state can be determined particularly simple and inexpensive.
  • the determined model-based theoretical state be corrected on the basis of at least one further actual value of the state of the compressor.
  • This further actual value preferably represents at least one pressure and / or one volume flow and in particular a measured suction pressure of the first stage and / or the second stage and / or a measured intermediate pressure and / or a measured one
  • thermodynamic model preferably compensates the determination of the theoretical state permanently by these further measured actual values, as a result of which the actual actual state of the compressor is as up-to-date and precise as possible in the actual state
  • the model-based correction is controlled directly by means of at least one uncorrected control value.
  • a predetermined state in particular, a state of
  • Compressor be understood in which a determination of the theoretical state by means of the model unit or the thermodynamic model would take too long, such as
  • an "uncorrected manipulated variable” should be understood here to mean, in particular, a manipulated variable which was determined independently of the thermodynamic model The uncorrected manipulated variable can be independent of the desired value
  • the predetermined state is a critical state of the compressor, which is converted by the direct control of at least one of the control elements in a non-critical state.
  • a critical state in particular a
  • a “non-critical state” is a state where the compressor is below the load limit
  • control values determined from the desired value or the determined control value for the actual state of the compressor are unadapted or no longer satisfy the actual state.
  • a preferred development consists in that at least one control value which is corrected as a function of the theoretical state and at least one uncorrected manipulated variable are interconnected via at least one comparator.
  • the comparator receives the at least one corrected manipulated variable from the control unit and the at least one uncorrected manipulated variable from a safety device, such as
  • a surge limit regulator for example, a surge limit regulator
  • Comparator can make a decision on the direct
  • Actuation of an applied actuating element can be realized structurally simple.
  • At least one of the uncorrected manipulated values actuate at least one valve.
  • the valve is preferably a continuous valve and particularly preferably a control valve. Through the valve can a
  • setpoint gradient This is under the phrase "change the setpoint above a
  • Determining the control values based on the target value by means of the optimization algorithm is incapable or unable to react quickly enough to this change. This value depends on a processing speed of the
  • Control unit is for example 0.5% / s.
  • model-based correction is triggered. Furthermore, it is advantageous if the direct control of at least one of the adjusting elements causes a faster adaptation of an actual value of the compressor to the desired value than by means of the model-based correction.
  • the actual value is
  • a final pressure of the compressor but in principle may be any other, the skilled worker considered useful actual value.
  • This direct control is done by means of
  • Control unit and based on at least one determined there uncorrected control value. This can be a mode of
  • provisionally still uncorrected control value passes quickly to adjust a state of the compressor to a new set point and thus to improve a workload of the compressor.
  • the compressor is controlled and the
  • Control preferably by means of a process controller, such as
  • Compressor and / or a position of a valve.
  • each guide device can be controlled with the same or with different control values.
  • a number of guide devices less than or equal to the number of stages of the compressor.
  • Value tables of maps are stored in the model unit. This could, for example, at a
  • a control value is a position of a valve and / or a rotational speed of the compressor. Consequently, it may further be advantageous if a
  • a further embodiment of the invention provides that a gas composition is measured and taken into account in the determination of the model-based theoretical state, whereby the determination or the thermodynamic model by, for example, inclusion of a real gas equation for operation with a non-ideal gas or on a
  • Model unit should be included in the determination and / or in the presence of at least one constant compressor field would be a determination of the gas composition based on at least one actual value or on the basis of measured quantities and the
  • the invention is further based on a compressor with a control unit and a model unit.
  • control unit be provided to determine at least two control values of at least two control elements of the compressor on the basis of a transmitted nominal value of a parameter of the compressor and that the
  • Model unit is provided to determine a model-based theoretical state of the compressor based on the control values and that the control unit is provided to at least one of the control values as a function of
  • the compressor 10 has a Variety Z or a first stage 64 and a second stage 66, which in each case a heat exchanger 68 for example to
  • Anstellwinkel ⁇ , a.2 of blades of the guide devices 56, 58 can be changed or adjusted.
  • the plurality Z of stages corresponds to a plurality Z of
  • Leitvortechnische 56, 58 The heat exchanger 68 of the second stage 66 downstream in the process in the flow direction 70 of a working fluid, not shown here, such as a gas, is a valve 52 in the form of a working fluid, not shown here, such as a gas, is a valve 52 in the form of a working fluid, not shown here, such as a gas.
  • Draining the fluid can be adjusted.
  • Non-return valve 76 is arranged, which separates the compressor 10 from another system not shown here. Before and during start-up of the compressor 10, the valve 52 is open and the fluid can escape, whereby in the compressor 10, a low pressure prevails. If a pressure above the pressure of the compressor 10 now prevails in the further system, the non-return valve 76 is kept closed. Now increases the pressure in the compressor 10 by a start-up of the compressor 10 and the closing of the valve 52 and the pressure exceeds a characteristic of the check valve 76, it is opened and the fluid can escape.
  • a plurality of measuring elements 78 for example in the form of temperature sensors, pressure transmitters and
  • volume flow V determined. Before the second stage 66, an actual value 34 of the suction temperature T 2 and an actual value 40 of a suction pressure P 2 are measured. Further, after the second stage 66 and in front of the check valve 76 is an actual value 42 one
  • the compressor 10 has a control unit 60 and a model unit 62, which operate a method for controlling the compressor 10.
  • a desired value 12 of a parameter 14 of the compressor 10 such as a
  • Mass flow m and thus m so ii transmitted to the control unit 60.
  • a process controller 80 in the form of a final pressure regulator, which has calculated the desired value 12 from the actual value 54 of the final pressure P E n d fed to it, whereby the compressor 10 is regulated and the desired value 12 is used as the controlled variable.
  • the process controller 80 receives a maximum value 82 of the control unit 60
  • Maximum value 82 is this as setpoint 12 to the
  • Control unit 60 given.
  • the control unit 60 now determines three control values 16, 18, 20 of the adjusting elements 22, 24, 26 or the guide devices 56, 58 and the valve 52 of the compressor 10 based on the desired value 12. This determination is carried out in a manner known to those skilled in the art by means of a The control unit 60 stored numerical algorithm in the form of a sequential quadratic programming. These three determined
  • Control values 16, 18, 20 are now transmitted to the model unit 62, which determines a model-based theoretical state of the compressor 10 based on the control values 16, 18, 20, wherein a behavior of the compressor 10 is simulated to determine the theoretical state
  • control unit 60 When the control unit 60 compares the parameter 30 or the determined mass flow m with the desired value 12 and, in the case of a deviation of the values from one another, uses the numerical method to correct the value
  • the parameter 30 compares the parameter 30 with other requirements, such as a distance to the surge limit SPG, a minimum load on individual pinion shafts of the compressor 10, a compliance with the absorption limit of the stages 64, 66, a
  • control values 16, 18, 20 on it are necessary, if necessary, the control values 16, 18, 20 on it.
  • Requirements may be stored in the control unit 60 and / or supplied from the outside.
  • Control values 16, 18, 20 are given again to the model unit 62 for determining the model-based theoretical state.
  • the behavior of the compressor 10 is gradually adjusted to the desired value 12, as in a control loop 28 between the control unit 60 and the model unit 62.
  • Control values 16, 18, 20 takes place only when the
  • Setpoint 12 corresponding parameter 30 of the theoretical state has reached a predetermined proximity to the setpoint 12.
  • thermodynamic model and the numerical algorithm. It is thus during operation of the compressor 10 constantly by variations of the three control values 16, 18, 20 and ⁇ , a. 2 and ß by the control unit 60 scenarios the
  • thermodynamic model or the model unit 62 sent.
  • the thermodynamic model determines and returns which theoretical state, for example based on the mass flow m, the efficiency ⁇ or the
  • thermodynamic model determines the effective
  • a molecular weight of the pumped fluid and a speed of the compressor 10 are assumed to be constant.
  • An overall pressure increase rges of the compressor 10 is composed of the pressure ratios ⁇ 1 , ⁇ 2 of the individual stages 64, 66 and is in accordance with
  • Compressor 10 is determined by:
  • Non-return valve 76 can be the position ß and thus the um- and / or blown off amount of fluid are taken into account and it follows:
  • control values 1 6, 1 8, 2 0, the angle of attack oii and c ⁇ 2 and the position ß are of the control elements 22, 24, 2 6th
  • ⁇ , T 2 , pi and p zw represent disturbance variables that depend on external boundary conditions.
  • the suction pressure pi can be assumed to be constant as a rule.
  • the model can determine the model-based theoretical state. Furthermore, however, the determined model-based theoretical state is corrected on the basis of further actual values 3 6, 38, 40, 42, the state of the compressor 10 or on the basis of the measured suction pressures pi, P 2 , the measured intermediate pressure p zw , and the measured volumetric flow V. ,
  • the compressor 10 has a safety device 84 in the form of a surge limit controller 8 6.
  • Pump limit controller 8 6 constantly determines whether a distance to the pumping limit S PG is maintained. For this he receives from the model unit 60 there theoretically determined parameter 30 of the distance of the pumping limit S PG and compares this with a stored in the surge limit 8 8 8 setpoint. If the parameter 30 approaches a range with, for example, 7%,
  • the comparator 50 now determines by comparing the
  • Control values 20, 48 which control value conveys a greater open position of the valve 52 and forwards this determined control value 20, 48 to the valve 52 for its control. Upon intervention of the surge limit regulator 86, this is
  • the uncorrected manipulated value 48 for example, the uncorrected manipulated value 48.
  • the actuator 26 or valve 52 is bypassed, bypassing the model-based correction directly by means of the uncorrected control value 48, whereby the
  • Compressor 10 is converted into a non-critical state and it is not operated at its load limit.
  • the surge limit regulator 86 is disengaged once the thermodynamic model has responded to the pressure change by adjusting its predictions.
  • Control value ßi St can be tracked.
  • the thermodynamic model thus has two functions; on the one hand the theoretical prediction of the state on the basis of the calculation with assumed control values 16, 18, 20 and on the other hand that of a control of the compressor 10 via the
  • the actuators 22, 24, 26, bypassing the model-based correction directly by means of uncorrected control values 44, 46, 48 driven.
  • this direct control of the adjusting elements 22, 24, 26 effects a faster adaptation of the actual values 34, 40, 42, 54 of the compressor 10 to the desired value 12 than by means of the model-based correction.
  • the control unit 60 thus determines during a large jump of the setpoint 12 during the
  • the energy savings can be via a display unit, not shown here for a
  • a control value 90 in the form of a rotational speed n of an actuating element 94, indicated only by dashed lines, in the form of a motor 96 can be determined, corrected and adjusted.
  • the actuator 94 in the presence of a predetermined state, can be controlled directly by means of an uncorrected manipulated variable 92, bypassing the model-based correction.
  • a control value 90 in the form of a rotational speed n of an actuating element 94 in the form of a motor 96 can be determined, corrected and adjusted.
  • the actuator 94 can be controlled directly by means of an uncorrected manipulated variable 92, bypassing the model-based correction.
  • thermodynamic model can be used instead of isentropic
  • Flow work or efficiencies can also be calculated with polytropic quantities.
  • other representations of the compressor map can be used, which allows a calculation of power and delivery quantity based on the given input variables.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Abstract

L'invention concerne un procédé pour commander un compresseur (10). Pour obtenir un bon rendement, ce procédé comprend les étapes consistant à : (a) transmettre au moins une valeur théorique (12) d'un paramètre (14) du compresseur (10), (b) déterminer au moins deux valeurs de régulation (16, 18, 20, 90) d'au moins deux éléments de régulation (22, 24, 26, 94) du compresseur (10) au moyen de la valeur théorique (12), (c) déterminer un état théorique du compresseur (10) sur la base d'un modèle à l'aide des valeurs de régulation (16, 18, 20, 90), (d) corriger de manière itérative au moins une des valeurs de régulation (16, 18, 20, 90) en fonction d'un état théorique, (e) commander au moins un des éléments de régulation (22, 24, 26, 94) au moyen de la valeur de régulation (16, 18, 20, 90).
PCT/EP2011/065662 2010-09-09 2011-09-09 Procéder pour commander un compresseur Ceased WO2012032164A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US13/820,812 US20130173063A1 (en) 2010-09-09 2011-09-09 Method for controlling a compressor
EP11757265.1A EP2598754A1 (fr) 2010-09-09 2011-09-09 Procéder pour commander un compresseur
CN201180043721.5A CN103097737B (zh) 2010-09-09 2011-09-09 用于控制压缩机的方法
RU2013115761/06A RU2570301C2 (ru) 2010-09-09 2011-09-09 Способ управления компрессором

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010040503A DE102010040503B4 (de) 2010-09-09 2010-09-09 Verfahren zur Steuerung eines Verdichters
DE102010040503.5 2010-09-09

Publications (1)

Publication Number Publication Date
WO2012032164A1 true WO2012032164A1 (fr) 2012-03-15

Family

ID=44651746

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/065662 Ceased WO2012032164A1 (fr) 2010-09-09 2011-09-09 Procéder pour commander un compresseur

Country Status (6)

Country Link
US (1) US20130173063A1 (fr)
EP (1) EP2598754A1 (fr)
CN (1) CN103097737B (fr)
DE (1) DE102010040503B4 (fr)
RU (1) RU2570301C2 (fr)
WO (1) WO2012032164A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015069841A2 (fr) * 2013-11-11 2015-05-14 Dresser, Inc. Système et procédé pour positionner des aubes de diffuseur variables dans un dispositif de compression
CN105443348A (zh) * 2015-12-23 2016-03-30 上海金自天正信息技术有限公司 气体压缩机系统
RU2675175C2 (ru) * 2016-08-09 2018-12-17 Вячеслав Николаевич Игнатьев Способ регулирования параметров компримированного газа и устройство для его осуществления
CN106368975B (zh) * 2016-11-25 2017-12-01 沈阳鼓风机集团股份有限公司 一种pcl压缩机性能控制方法及装置
ES2905429T3 (es) * 2017-04-27 2022-04-08 Cryostar Sas Método para controlar un compresor de varias cámaras
CN108009382B (zh) * 2017-12-25 2021-09-24 沈阳鼓风机集团股份有限公司 离心压缩机设计系统
CN108073772B (zh) * 2017-12-25 2021-06-22 沈阳鼓风机集团股份有限公司 离心压缩机设计方法
EP4542039A1 (fr) 2023-10-20 2025-04-23 Burckhardt Compression AG Procédé de commande d'un système de compresseur

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EP1069314A1 (fr) 1999-07-16 2001-01-17 Abb Research Ltd. Commande d'une unité-compresseur
EP1298512A2 (fr) * 2001-09-26 2003-04-02 Coltec Industries Inc. Modèle adaptif, aéro-thermodynamique d' un moteur
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DE102008005354A1 (de) * 2008-01-21 2009-07-23 Man Turbo Ag Verfahren zur Regelung einer Strömungsmaschine
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Publication number Priority date Publication date Assignee Title
DE19506790A1 (de) 1994-02-28 1995-09-21 Kuehnle Kopp Kausch Ag Verfahren zum wirkungsgradoptimierten Betreiben eines Radialverdichters
EP1069314A1 (fr) 1999-07-16 2001-01-17 Abb Research Ltd. Commande d'une unité-compresseur
EP1298512A2 (fr) * 2001-09-26 2003-04-02 Coltec Industries Inc. Modèle adaptif, aéro-thermodynamique d' un moteur
US20070118270A1 (en) * 2005-11-18 2007-05-24 General Electric Company Sensor diagnostics using embedded model quality parameters
US20070179763A1 (en) * 2006-01-27 2007-08-02 Ricardo, Inc. Apparatus and method for compressor and turbine performance simulation
DE102008005354A1 (de) * 2008-01-21 2009-07-23 Man Turbo Ag Verfahren zur Regelung einer Strömungsmaschine
US20090274565A1 (en) 2008-05-02 2009-11-05 White Robert C Continuing compressor operation through redundant algorithms

Also Published As

Publication number Publication date
US20130173063A1 (en) 2013-07-04
CN103097737A (zh) 2013-05-08
CN103097737B (zh) 2015-06-03
RU2570301C2 (ru) 2015-12-10
RU2013115761A (ru) 2014-10-20
DE102010040503A1 (de) 2012-03-15
DE102010040503B4 (de) 2012-05-10
EP2598754A1 (fr) 2013-06-05

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